Duplex automatic setting-up machine



June 4, 1957 w. R. LINDSAY ETAL 2,794,373

DUPLEX AUTOMATIC SETTING-UP MACHINE Filed Jan. 26, 1954 7 Sheets-Sheet 1 14 zz 2.6 f/

INVENTORS Z/JaR mm ATTORNEYS June 1957 w. R. LINDSAY ETAL 2,794,373

DUPLEX AUTOMATIC SETTING-UP MACHINE Filed Jan. 26, 1954 "7 Sheets-Sheet 2 F N x m INVENTORS m WM A? m; $35M.

I y ATTORNEYS June 4, 1957 w. R. LINDSAY ETAL DUPLEX AUTOMATIC SETTING-UP MACHINE 7 Sheets-Sheet 4 Filed Jan. 26, 1954 L TTJ B 64% MATTORNEYS June 4, 1957 w. R. LINDSAY ETAL 2,794,373

DUPLEX AUTOMATIC SETTING-UP MACHINE Filed Jan. 26, 1954 7 Sheets-Sheet 5 INVENTORS N c: wMa/PILA;

AfiORNEYs June 4, 1957 w. R. LlNDSAY ETAL 2,794,373

DUPLEX AUTQMATIC' SETTING-UP MACHINE w INVENTORS BY w izm;

ATTORNEYS June 4, 1957 w. R. LINDSAY ETAL 2,794,373

7 DUPLEX AUTQMATIC SETTING-UP MACHINE Filed Jan. 26. 1954 7 Sheets-Sheet '1 INVENTORS United States Patent DUPLEX AUroMArIe SE'ETWG-UP MAen'rN n Wallace R. Lindsay and Robert F. Stewart, Amsterdam, N. Y., assignors to Inman Manufacturing Company, Inc., Amsterdam, N. Y., a corporation of New York Application January 26, 1954, Serial No. 406,168

19 Claims. (Cl. 93-51) This invention relates to automatic box-making machines and particularly to a box-making machine of the type in which a succession of single blanks are automatically fed from a source of supply and then transferred through a gluing mechanism to a forming mechanism where upon completion of the forming step a finished box is discharged from the machine. The invention relates more particularly to an automatic box-forming or setting-up machine of the two-production line type which comprises two forming mechanisms lying in transverse alignment or juxtaposition with means for feeding a succession of box blanks to each of the forming mechanisms and means for alternately actuating said forming mechanism to fold and press said blanks into box form.

It is the primary object of the present invention to provide a box-forming machine which is designed and constructed in such a manner that the transversely aligned forming mechanisms, as well as the feeding, transfer, and gluing mechanisms are driven from a single source of power. Moreover, these mechanisms are designed and constructed to alternately feed and transfer successive blanks from each of the two production lines in timed relation with the alternate actuation of the forming mechanisms whereby the blanks are folded and formed into boxes.

Machines of the type described which comprise two production lines are generally constructed so that a blank moves simultaneously through the same sequence of steps in each production line, i. e., blanks in both lines are simultaneously fed to the forming mechanism, which forming mechanisms are simultaneously actuated to fold the blanks into box form. In this type machine pressure plates are arranged to act against opposite ends of a box form to press side and end panels, to which adhesive has been applied, into contacting relation. A single cam drive is arranged to force these pressure plates against the box form. Difficulties are encountered in this type construction bringing uniform pressure to bear against the box forms. This is particularly true where feed has been interrupted on one of the production sides and no blank is positioned over the forming die. When the pressure plates are actuated toward the box-forming position, the pressure plates do not encounter a resistance on the side of the empty die to balance the stroke of the die on the other side until the pressure plate on the empty side encounters the head of the plunger, which moves into the die prior to the movement of the pressure plates toward box-forming position. It is apparent, therefore, that due to this unresisted stroke of the pressure plates in the one production line, irregular pressure is applied to the box contained in the die on the other side. It is, therefore, another object of this invention to provide a machine having independently acting working mechanisms in each production line with a novel die construction by which the above difi'iculties are obviated.

Machines of the general type described comprising two production lines have been suggested in which the forming mechanism is hydraulically operated and more particularly in which the die engaging plungers are reciprocated hydraulically. Such a' machine is disclosed in Patent No. 2,620,711 issued December 9, 1952, to Wallace Lindsay, one of the co-inventors of the present machine. Dilficulties in this type machine have been encountered in bringing about proper timing between the delivery of a blank to the forming die and the movement of the plunger into die engaging and box-forming position.

Additional difiiculties are encountered due to the heavy and noisy pounding or hammering attributable to the rapid and simultaneous movement of the hydraulically operated plungers in one same cycle, as well as the great stress placed on the machine due to this simultaneous movement of the plungers. It is, therefore, another object of the present invention to provide a box-forming machine in which the plungers can be alternately and mechanically driven at high-speed with great efiiciency to not only obviate the above-mentioned undesirable hammering but also to maintain a dynamic balance in the machine.

Another object of the present invention is to provide a novel mounting and drive arrangement for the reciprocating plungers and one in which the length of the plunger stroke can be adjusted in accordance with the depth of the box to be formed.

It is another object of this invention to provide a die mechanism in which the ends of a folded box blank, which are to be glued together, are held in contact with pressure means through a substantial part of the forming step.

A further object of the present machine is to provide a novel feeding mechanism whereby blanks can be alternately fed to the transfer mechanism in timed relation to the working movement at the forming end of the two production lines.

Other objects and advantages will be apparent from the following more detailed description of a preferred embodiment of the present invention read in connection with the accompanying drawings in which:

Figure 1 is a top plan view of the present machine;

Figure 2 is a longitudinal sectional view taken along lines 22 of Figure 1 showing the feeding and gluing mechanism;

Figure 3 is a vertical section view taken along the line-s 3-3 of Figure 2;

Figure 4 is a detail vertical longitudinal section show ing the sucker actuation mechanism;

Figure 5 is a similar view of the feeding slide and mechanism for actuating same;

Figure 6 is a vertical transverse sectional view taken along the line 6--6 of Figure 5;

Figure 7 is a side elevational view of the entire machine;

Figure 8 is an end elevational view of the right hand end of Figure 7 showing the feeding mechanism;

Figure 9 is an end elevational view showing the forming mechanism;

Figure 10 is a longitudinal, vertical sectional view of the box-forming mechanism;

Fig. 11 is a horizontal sectional view taken along the lines 1111 of Figure 10;

Figure 12 is a vertical transverse sectional view taken along the lines 12l2 of Figure 10;

Figure 13 is an elevational view taken along the lines 13-13 of Figure 10;

Figure 14 is a top plan view of a box-forming die;

Figure 15 is a view of a box blank;

Figure 16 is a view of a box blank in partly folded position; and

Figure 17 is a view of a completed box.

The box-forming machine of the present invention is designed and constructed to provide dual production lines which in a large part may be operated by common actuating mechanism and at the same time arranged so that the production lines are largely independent of one another. Thus a derangement in one production line will not interfere with efiective production in the other. Since the operation of the mechanism of the two production lines is similar to a large extent, the following description will apply to a single production line except in those instances Where the operation of the lines is different. In such places it will facilitate a better understanding of the operation of the machine to describe both production mechanisms.

The blanks which are to be formed into boxes are designated generally by the reference numeral and are illustrated in Figures through 17. As can be seen, the blanks contain a bottom panel 11, side panels 12 and 13 and end flaps 14 and 15. The side panels 12 and 13 also have corner flaps 16, 16 and 17, 17 respectively. To facilitate the forming of the boxes, the blanks may be scored or pre-cut on the lines intermediate the panels which are to be folded as illustrated in Figures 15 and 16.

. The blanks to be processed are stacked one on top of the other and lie on a feed platform adjacent one end of the machine designated as A in the top plan view in Figure 1. Individual blanks are successively fed from the bottom of the feed stack onto a transfer conveyor. The transfer conveyor carries the blanks through a gluing mechanism, designated as B, at which point glue is deposited on the end flaps 14 and 15 of the blanks. The transfer conveyor then carries the blanks forward of the gluing mechanism at which point they are engaged by a high-speed conveyor which positions the blank over an expansible and contractible box-forming die mechanism, shown at C in Figure 1. The blanks are then engaged by a reciprocating plunger which forces them through the forming die at which point the end flaps are firmly pressed against the side corner flaps of the blank thus forming the finished box.

For the most part, the operating mechanism of the present machine is mounted on a rigid frame 18 which frame comprises parallel side frame members 19 and 20. These side frames are made in panels to permit the machine to be disassembled to facilitate handling and transporting. Other parts of the frame will be referred to as the individual working mechanisms of the machine are discussed.

Blank feeding mechanism Each production line of the machine is provided with a blank rack which comprises brackets 21 and 22 which extend transversely of the machine having their ends supported on the respective side frame members 19 and 20. Brackets 21 and 22 have slots 23 and 24 respectively extending longitudinally therein. Brackets 25 and 26 extend between and are supported on brackets 21 and 22 by means of pins extending through the longitudinal slots 23 and 24, and can thus be adjusted relative to each other. Two pair of upright guiding brackets 27, 27 and 23, 28 (Figure 2) are adjustably mounted on the brackets 25 and 26, respectively. These guiding brackets are adjustable longitudinally with respect to the machine as a whole and it is thus readily seen that with the transverse adjustment of brackets 25 and 26 and the longitudinal adjustment of guiding brackets 27 and 28 any size blank, which it is desired to be used, can be accommodated between these brackets.

As is shown best in Figure 3, a supporting rod 29 is adjustably mounted in slots 30, 30 which are provided in the upstanding brackets 31, 31. These brackets are mounted on a plate 68 carried between side frames 19 and 20 of the main frame. A supporting plate 32 overlies and is supported adjacent to one end thereof by rod 29 and at the other end by angle member 33 Will Chis secured to plate 68 of the main frame. A back support 34 is mounted on bracket 35 which bracket is adjustably supported on brackets 25 and 26 by means of pins extending through the longitudinal slots in brackets 25 and 26. The back support member 34 is secured to a supporting angle piece 36 which has a pin extending through a slot in bracket 35. A stack of blanks can thus be supported on the supporting plate 32 with the back edges thereof abutting the back support 34.

The feeding mechanism for each production line as illustrated in Figures 2, 4 and 5 comprises a pair of sucker members 37, 33 mounted for actuation into and out of engagement with the lowermost blank :39 of the stack. The suckers 37, 38 are mounted adjacent the ends of arms 49 and 41, respectively, the other end of said arms being secured to a shaft 42. Shaft 42 spans substantially the entire width of a production line and has its ends journalled in brackets 43, 44, upstanding from plate 68 of the main frame. An arm 45 is secured'to shaft 42 adjacent one end thereof with a second arm or link 46 being pivoted at 47 to the other end of arm 45. A cam follower arm 48 is pivotally connected at the lower end of arm 46 as at 49. As can be seen particularly in Figure 4 the length of arms 45, 46 and 48 can be adjusted by means of expansion mechanisms Sll, 51 and. 52, respectively. Arm 48 is pivotally mounted at 53 to a bracket 54 which is secured to a bracket 55 extending downwardly from the main frame. A cam 56 is mounted on a cam shaft 57 for rotational movement. therewith, the rotational drive for the cam shaft being described at a later point herein. The free end of carn follower arm 48 is supported by cam 56 and is held in engagement therewith by means of a spring 59 (Figure 2) which has one end secured to bracket 61 on arm 48 remote from the free end thereof.

It can readily be seen that as the cam shaft 57 is rotated in a counter-clockwise direction cam 56 causes arm 48 to rock about its pivot 53. The rocking movement of arm 48 pulls link 46 upwardly and downwardly thereby imparting an oscillating motion to shaft 42 through arm 45. Suction members 37, 38 are thereby swung through an arc toward and away from the supply of blanks resting on the blank rack. The actual length of this are can be regulated by adjusting the length of arms 45, 46 and 48 by means heretofore mentioned.

the suckers, through lines 64 as hereinafter described' In the preferred embodiment each production line is provided with three feed rolls 65 which are mounted on shaft 66. It will be understood, of course, that any number of these rolls as might be expedient could be used. Shaft 66 has its ends .journaled in the side frames 19 and 20 of the main frame. A slide 67 is mounted on plate 68 of the main frame for longitudinal movement thereon and has upstanding side brackets 69 and 69' (Figure 6) with a rod 70 journaled at its ends in sleeves 71 and 71' which are mounted in cut away portions of these side brackets. Springs 72 and 72 are also mounted in the cut away portions of side brackets 69 and 69' to bear against sleeves 71, 71' and thereby urge rod downwardly toward rolls 65. A link 74 is pivotally connected at 75 to a flange 73 which extends rearwardly from slide 67. Link 74 is also pivoted intermediate its ends at 76 to a support 77 which is secured to and extends downwardly from angle iron 55 mounted on the underside of plate 68 of the main frame. A disk 79 having an internal'cam groove 80 is mounted on cam shaft 57. A small roller or pin 81 is mounted on the free end of arm 77 and rides in cam groove 80. As shown best in Figure 5, the cam groove '80 is designed and constructed as to cause swinging movement of arm 77 about its pivot 76 upon rotation of the cam shaft 57. This swinging movement of arm 77 thus imparts a reciprocating movement to the slide 67 thereby moving it to and from with respect to the rolls 65 and the stack of blanks.

In operation the valve 63 is automatically set to effect a suction through the suction members 37, 38 when in its full line position of 'Figure 4. As the cam 56 rotates to a point where its high point 58 engages cam follower arm 48, the suction member 37 is in its full line position of Figure 4 and in engagement with the lowermost blank 39. At the same time the slide 67 is adjacent its fartherest forward point. As the shaft 57 continues to turn, the suction member 37 will swing downwardly thus bending the front portion of blank 39 downwardly over the front edge 82 of the blank supporting plate 32. As the edge of the blank 39 engages the upper periphery of rolls 65, the slide 67 has been moved through its cam linkage to a position shown in Figure 2, in which position the forward edge of blank 39 is initially gripped between rod 70 and rolls 65. At the moment the forward edge of blank 39 is gripped between the rod and the rolls, valve 63 cuts off the suction to suction member 37. It is apparent, therefore, that as the slide moves to frictionally grip, a blank between rod 70 and rolls 65, the rotary action of rolls 65 will shoot the blank between the rod and the rolls forwardly onto the transfer conveyor 83.

The feeding mechanism for both production lines operates in a similar manner, however the actuating mechanisms of the separate feeding mechanisms are arranged to alternately feed blanks to the transfer conveyors of the separate production lines. To effect this alternate feeding, the cam 56' of the other feeding mechanism not previously described is displaced 180 in phase from the cam 56 of the first feeding mechanism, i. e., when the high point 58 of cam 56 is in its uppermost position, the high point 58' of cam 56 is in its lowermost position. As can be seen in Figure 8, this cam 56' is also mounted on cam shaft 57. Likewise a disc 79' is mounted on cam shaft 57 with an internal cam-groove 80 of a similar contour as groove 80. Disc 79', however, is also displaced 180 in phase with respect to the disc 79. It can readily be seen, therefore, that as the cam shaft 57 rotates, the sucker members of the two feeding mechanisms are alternately brought into contact with the lowermost blank on the supply stack of the respective line, while the slides 67 and 67' of the two mechanisms are alternately reciprocated in timed relation with the sucker members to effect an alternate feeding of blanks from the supply stacks of the two production lines.

The delivery end of the main delivery conveyor 83 is carried on sprocket 84 mounted on shaft '85 which has its ends journaled in the side frame members 19 and 20, respectively. The forward end of the conveyor 83 is supported on sprocket 86 mounted on the shaft 87 which shaft is also journaled in side frame members 19 and 20,- r'espective'ly. An idler '88 is adjustably mounted on the main frame and acts to take up any slack in the main conveyor chain. Drive is imparted to the conveyor chain through shaft 84 as will be hereinafter described. The conveyor chain 83 has upstanding lugs 89 which act to carry the blanks forward along the production line. As best seen in Figure 1, it extends longitudinally of the machine guided by chain guides 90 and is positioned to support the blanksintermediate their side edges. The edges of the blanks being transferred are supported on longitudinally extending angle irons 91' and 92, which are carried by the main frame.

Gluing mechanism The delivery chain 83 carries the blanks from the feeding mechanism next to the gluing mechanism. The gluing mechanism may be of any known type, with the 6 embodiment illustrated in Figures 2 and 7 comprising an applying roller 93, a distributing roll 94 and a backing roll 95. The backing roll has a shallow groove intermediate its ends to allow the conveyor chain 83 to pass therethrough. The distributing roll 94 is mounted along with a glue pot 95 on a movable platform '96 which is supported on the bracket 97 of the main frame. A hand wheel 98 through a threaded stud 99 effects adjustable movement of the distributing roll 94 carried on the slide with respect to the application roll 93. Pads 100 are selectively carried along the outer circumference of the applying roll 93, which pads engage the end panels 14 and 15 of the box blank as it passes between the application roll 100 and the backing roll 95 to deposit a layer of glue on these end panels. As shown in Figure 2, one or more conventional stripper wires .101 suitably mounted on the main frame between brackets 201 (of which only one is shown) prevent the blank from adhering to and following the path of application roll 93.

Blank positioning As the blank passes from the gluing mechanism, it is carried forward by conveyor chain 83 toward the forming mechanism. As can be seen best in Figure 10 the conveyor chain 83 extends to a point just short of the forming mechanism. A high speed conveyor mechanism comprising conveyor chains 102 and 103 which lie in a path above the guiding channels 91 and 92 are mounted on sprockets 104 and 105, respectively, at their end being toward the feeding end of the mechanism and sprockets 106 and 107 at their end adjacent the forming mechanism. Sprockets 104 and are mounted on shaft 186 which has its ends journalled in brackets 187 and 187 which are secured to the side frame members 19 and 20. Sprockets 186 and 107 are mounted on stub shafts 188 and 188 which are journalled to brackets 189 and 189 secured to the outside of angle irons 91, and 92. Drive is imparted to the high-speed conveyor chains through shaft 186, as will be hereinafter described. Lugs 108 and 109 on the high-speed conveyor chains 102 and 103 extend downwardly as the chain moves along its lower run as shown in Figure 10. These lugs 108 and 109 are adjustably mounted so that they will contact the side panel corner flaps 16 and 17 of the box blank, respectively, to throw the blank forwardly and position the blank over the box-forming die mechanism which mechanism is designated generally by the reference numeral 110. Inclined cams 111 are mounted on the outer sides of angle irons 91 and 92 adjacent the forward end of the die forming mechanism and are engaged by a camming surface on lugs 108- to guide these lugs upwardly away from the end of the box blanks to thereby allow the lugs to pass over the blank which has been positioned over the box-forming die. A stop 112 is mounted on transverse bracket 126, which lies adjacent the rearward end of the box forming mechanism to stop the forward movement of the blanks to thereby positioning them over the forming die.

Box-forming mechanism The die-forming mechanism of each production line of the present box-making machine comprises a pair of mutually facing slides 113 and 114 mounted on bed plate 115 of the main frame. The slides comprise elevated side members 116 and 117 and a series of rollers 118 lying one above the other having their ends journalled in the side members. Backing plates 119 and120 are also carried by the slides and extend upwardly from the bed plate 115. Angular brackets 121 and 122 are adjustably mounted on the bed plate 115 and springs 123 and 124 are carried between these angular. brackets 121 and 122 and backing plates 119 and 120, to urge the slides 113 and 114 toward each other. Brackets 125 and 126 lie transversely of the die forming mechanism and are supported on posts 127 extending upwardly from the bed plate 115. Brackets 128 and 129 are adjustably mounted onrbrackets 125 and 126 by means of pins extending downwardly from adjacent the ends of these brackets through longitudinal openings in the transverse bracket members 125 and 126. Brackets 128 and 129 have secured thereto by means of bolts 130 or other suitable securing means, a plurality of downwardly extending guide plates 131 and 132. In the preferred embodiment, three such plates are mounted on each bracket. It should be understood, of course, that any number of these guide plates can be placed adjacent each other or a single larger guide plate can be used. These guide plates are rigidly held in place and have cut-away portions 133 and 134 adjacent their lower ends for purposes hereinafter described. A die well is thus formed whose periphery is defined by the downwardly extending plates 132 on two sides and the surface of the rollers 118 on the other two sides. As can be seen in Figure 12 adjustable guide brackets 135 and 136, which are extended portions of angle plates 91 and 92, however with their horizontal carrying surfaces cut away, act to guide the sidewise movement of the blanks. The ends of these guide brackets 135 and 136 are adjustably supported on slotted brackets 125 and 126 to allow for different widths of the blanks. As previously mentioned, stop member 112 is carried by bracket 126 and regulates the lengthwise movement of the blanks.

Plungers 137 and 138 are positioned in vertical alignment with the respective die wells and are mounted for reciprocating movement into and out of such wells. The plungers are mounted on toothed racks 139 and 140, the teeth 141 and 142, respectively, of which are held in meshing relation with a pair of driven gears as hereinafter described. Flanges 192 and 193 are secured as by welding or other conventional means to the lower ends of racks 139 and 140, respectively, with plungers 137 and 138 being detachably secured to these flanges by known means such as bolts or screws. The frame of the machine has extensions 143 and 144 upstanding from the side panels 19 and 20 with an end panel 145 being supported intermediate these upstanding side extensions. A gear 151 is mounted on shaft 152 which has its ends journalled in brackets 153 and 154, respectively, carried by the back panel 145. These brackets 155 and 156 are secured to panel 145 by any suitable means such as bolts, screws or the. like. A drive rack 146 which has one end eccentrically mounted in a manner hereinafter described to a rotating disc 148 extends through and is guided by a bracket 157 mounted on back panel 145 with teeth 149 adjacent the upper end of the drive rack thereby held in meshing relation with gear 151. A secnd gear 158 is mounted on shaft 152 and is in meshing relation with teeth 142 of plunger rack 140. A guide bracket 159 is secured to the back plate 145 and acts to guide the plunger rack 149 to maintain meshing relation with the gear 158. A second shaft 160 has its ends journalled in brackets 161 and 162 which brackets are also secured to back plate 145 by any conventional means, such as bolts or screws 156. A gear 163 is mounted on shaft 160 intermediate its ends and is in direct mesh with a gear 164 carried by the first mentioned shaft 152. A second gear 165 is mounted on shaft 160, this gear being in driving relation with the plunger rack 139 through teeth 141 on the rack. A guiding bracket 166 which is mounted on back plate 145 acts to guide and maintain the rack 139 in meshing relationship with the gear 165. It is apparent therefore that as the disc 148 is rotated, by means which will hereinafter be set forth, a reciprocating motion is imparted to the eccentrically mounted drive rack 146. This reciprocating motion imparts an oscillating motion to shaft 152 which motion is directly translated to plunger rack 148 through gear 158 to impart a reciprocating motion to plunger 138. Through gear 164 of shaft 152 and gear 163 of shaft 160, the oscillating motion of shaft 152 is translated to shaft 160 thus imparting an oscillating motion to shaft 160 8 however in an opposite sense from the motion of shaft 152. This oscillating motion of shaft is translated through gear to impart a reciprocating motion to plunger rack 139 and plunger 137. It can be seen therefore that the plunger 137 is reciprocated in. an opposite sense from plunger 138, i. e., while plunger 138 is in its downward strokepplunger 137 is in its upward stroke.

The mounting of. drive rack 146 on disc 148 is effected by positioning a block 166 within a cut-away portion 167 in said disc. The block is adjustably secured to the disc by means of a bolt or the like extending through slots 168 in the block into the disc. The end of drive rack 146 is mounted to block 167 by means of a pin 169. With the adjustability of drive rack 146 radially with respect to disc 148, it can be seen that the length of the stroke of the drive rack can thus be adjusted and the effective stroke .of plungers 137 and 138 thereby length ened or shortened.

In operation, when a box blank has been positioned over the forming die, the plunger head 137 moves downwardly toward said die as shown in the left side of Figure 12. At the same time, plunger 138 has just completed its downward travel which efiected the formation of the box 170. As the plunger 138 moves in its upward travel the top edges of the box engage the shoulders formed by the cut-away portions 133 and 134 of the side plates 131 and 132 to thus prevent the box from being carried upward by the plunger. On the next successive downward stroke of plunger 138 a newly formed box will force box 170 through the die well into a receiving bin or onto a conveyor its the case may be. While plunger 138 moves upwardly, plunger 137 is at the same time moving downwardly into a blank engaging position. As the plunger makes its initial contact with the box blank 10 the end flaps 14 and 15 are deflected upwardly as shown in Figure 16 as they contact folding fingers 171 and 171, respectively, and at the same time the corner flaps 16, 16 and 17, 17 engage folding fingers 172 and 173, respectively, to initiate a slight folding action on these corner flaps as shown also in Figure 16. Continued downward movement of the plunger 137 forces the box blank through the well with side flaps 12 and 13 being engaged between the guide plates 132 and 131, respectively, and the sides of the plunger, while the end flaps 14 and 15 are brought into contact with the rolls 118. At this point, the corner flaps 16, 16 and 17, 17 have been forced within the end flaps 14 and 15 and lie between these end flaps and the ends of the plunger. The pressure exerted by the rolling action of rolls 118 as the box moves through the well thus glues these ends and side corner flaps together. It should be pointed out that the slides carrying the rollers 118 upon the initial movement of the plungers are extended inwardly toward each other to the full extension of springs 123 and 124. Thus as the boxes are forced into engagement with the rolls 118' the slides are forced outwardly against the pressure of springs 123 and 124, thus effecting the pressure rolling and pressing of the glued end flaps into contact with the side corner flaps.

From the foregoing description, it will be apparent that our machine may be adapted to form a variety of differently shaped and sizedboxes. For instance, with the adjustability of the effective plunger stroke boxes may be formed which have higher or lower upstanding end panels 14 and 15. Likewise, boxes may be formed in which either or both side panels 12 or 13 extend above those shown by way of example. Also the end corner flaps may be of any size or shape within the confines of the lengths of the side and end panels. By adjusting brackets 128 and 129 which carry guiding plates 132 and 131 and bracket 121 and 122 which bear against slides 113 and 114, it can readily be seen that the dimensions of the die well can bechanged toaccommodate various size box blanks and corresponding plunger-s to thus form many size boxes.

From the foregoing description it will also be appareat that the failure to feed or the jammingof blanks in one production line will not affect the timing or the effective operation of the working mechanism of the other production line. On the other hand, since the drive is unitary to the working mechanism of both lines as described in detail below, the timing problem which arises in many machines of this general type is eliminated.

Drive mechanism The drive for the instant machine for the most part comprises conventional drive means such as belt and pulley mechanisms or sprocket and chain mechanisms which translate drive to and from the various shafts as set forth below. Drive is initiated through a motor 174 mounted on the bottom panel of the main frame. Drive is taken from stub shaft 175 of the motor to shaft 179 which is journaled between the side frame members. Drive is taken from shaft 179 to shaft 180 of a conventional gear reducing mechanism and also directly to shaft 181 of the suction pump 62.

A jack shaft 183 is journaled in the side frame members and is driven from shaft 182- of the gear reducer. Drive is taken from the jack shaft to cam shaft 57 of the feeding mechanism, to the conveyor chain 83 of the transfer mechanism, and to the backing roll 95 of the gluing mechanism. Drive is then taken from cam shaft 57 to shaft 66 of the feed rolls.

The drive for the forming end of the machine is also taken from the main motor 174 through the gear reducer mechanism. Drive is taken from shaft 182 to shaft 184, which has one end journaled in side frame 19 and the other end in bracket 190, upstanding from longitudinal supporting plate 191 of the base frame. Disc 148, which drives the plunger rack 146 is mounted on this shaft 184. Drive for the high-speed conveyor is also taken from shaft 184 through shafts 185 and 186 and meshing gears carried by the last two mentioned shafts. From the foregoing description of the drive mechanism, it is apparent that the drive for all the working mechanisms of both production lines of the machine is taken from a single source of power thus obviating any timing difiiculties which might occur in multi-drive machines.

The box-forming machine as illustrated and described above in connection with a preferred embodiment thereof is by Way of example only and any changes which might occur to one skilled in the art are contemplated by the present invention, within the scope of the following claims.

Having thus described the invention, what is claimed as new and desired to be secured by Letters Patent is:

l. A box-forming machine comprising two forming mechanisms in transverse alignment, means for alternately feeding box blanks to each of said mechanisms, means adjacent said feeding means for applying adhesive to said blanks before arrival at said forming mechanisms, and means alternately actuating said forming mechanisms to fold and press said blanks into box form.

2. A box-forming machine as defined in claim 1 in which each said forming mechanism includes a plunger and said last mentioned means comprises a reciprocable member, means for reciprocating said member, and means operatively connecting said plungers to said reciprocable member for simultaneous movement in opposite directions.

3. A box-forming machine as set forth in claim 2 in which said last mentioned means comprises a pair of shafts operatively connected to said reciprocable member for simultaneous rotations in opposite senses, and means operatively connecting said respective plungers to said respective shafts.

4. A box-forming machine as set forth in claim 2 in which said means for driving said reciprocable member includes a rotating disc, said reciprocable member having one end eccentn'cally mounted on said disc, and means to radially adjust said one end on said disc to thereby 10 effectively lengthen 'or shorten the stroke of said recipro' cable-.member.

5. A box-forming machine as set forth in claim 1 in which said forming mechanism includes a plunger and said last mentioned means comprises a reciprocating drive rack, a plunger rack connected to each said plunger, and means operatively connecting said plunger racks to said drive rack to give simultaneous movements in opposite" directions.

6. A box-forming machine as set forth in claim 5 in which said last mentioned means comprises a pair of shafts operatively connected to said drive rack for simultaneous rotation in opposite senses, gear means connecting one said shaft to one of said plunger racks and gear means connecting the other of said shafts to the other said plunger rack.

7. A box-forming machine comprising two forming mechanisms in transverse alignment, each of said mechanisms including a plunger and a cooperating expansible and contractible forming die mechanism associated with said plunger, means for alternately feeding box blanks to each of said mechanisms, means intermediate said feeding means and said forming mechanism for applying adhesive to at least a part of said blanks, and means" for alternately moving said plungers into and withdrawing them from cooperating relation with their respective die mechanisms to fold and press said blanks into box form, said die mechanisms being alternately expanded and contracted responsive to such alternate movement of their respective plungers into and withdrawal thereof from cooperating relation with said die mechanisms.

8. A box-forming machine as set forth in claim 7 in which said die mechanism comprises means for initiating a folding action on said blanks and means for pressing said glued portions of said blank into contact with other portions of the folded blank.

9. A box-forming machine as set forth in claim 8 in which said pressing means comprises a slide, a series of rollers mounted on said slide and means urging said rollers toward said box whereby said folded portions of said blank are adhesively pressed together.

10. A box-forming machine as set forth in claim 9 and, in addition thereto an adjustable backing support, said urging means comprising at least one compression spring mounted between said slide and said backing support.

11. A box-forming machine as set forth in claim 1 in which said feeding means comprises means for supporting two stacks of blanks and dual means including air conducting means for alternately detaching blanks from said respective stacks and forwarding said blanks to said respective forming mechanisms.

12. A box-forming machine as set forth in claim 11 in which said dual means comprises sucker means, vacuum means connected to said sucker means, means for alternately moving one of said sucker means successively into contact with the lowermost blank in one of said stacks and then to a position adjacent one of said forwarding means, and means for moving the other of said sucker means successively into contact with the lowermost blank in the other said stack and then to a position adjacent the other said forwarding means.

13. A box-forming machine as set forth in claim 12 in which said means for moving said sucker means includes means for moving said one of said sucker means, comprising a rotating shaft, a cam mounted on said shaft, a second rotatable shaft, said one of said sucker means including at least one sucker member mounted on said second shaft and linkage means connected to said second shaft, said linkage means operatively engaging said cam for actuating movement thereby to thus impart an oscillating movement to said second shaft.

14. A box-forming machine as set forth in claim 13 in which said means for moving said sucker means includes means for moving said other of said sucker means, comprising a second cam mounted on said first mentioned shaft, however displaced 180 in phase from said first mentioned cam, afurther rotatable shaft, said other of said sucker meanscomprising at least one sucker member mounted on said further rotatable shaft and a second linkage means connected to said further shaft, said second linkage means operatively engaging said second cam for actuating movement to impart an oscillating movement to said further shaft.

15. A box-forming machine as set forth in claim 12 in which said dual means includes feeding rolls, means for rotating said rolls, and dual means for alternately pressing said lowermost blank of one of said stacks against said feeding rolls at a point when said one of said sucker means is in its said adjacent position and means for pressing the lowermost blank of said other stack against said feeding rolls at a point when said other of said sucker means is in its said adjacent position.

16. A box-forming machine as set forth in claim 15 in which said means for pressing the lowermost blank of one of said stacks comprises a reciprocable slide, means for reciprocating said slide, means on said slide for pressing said blank against said feed rolls, and means for moving said slide into and out of blank engaging position.

17. A box-forming machine as set forth in claim 16 in which said pressing means comprises a rod, said rod being rotatably mounted on said slide, whereby said blank is 'frictionally gripped between said feed rolls and said rod upon movement of said slide into blank engaging position. i 18. A box-forming machine as set forth in claim 16 in which said means for reciprocating said slide comprises a rotating shaft, a cam mounted on said shaft, and a linkage means operatively associated with said slide and said cam for imparting reciprocating motion to said slide.

19. A box-forming machine as set forth in claim 18 in which said means for pressing the lowermost blank of said other said stack comprises a slide, a rotatable rod carried by said last mentioned slide, means to move said last mentioned slide into blank engaging position, and last mentioned means comprising a second cam mounted on said rotating shaft, however displaced in phase from said first mentioned cam, and a linkage means operatively associated with said last mentioned cam and said last mentioned slide for imparting reciprocating motion to said last mentioned slide.

References Cited in the file of this patent UNITED STATES PATENTS 1,067,253 Inman July 15, 1913 2,321,562 Coy et a1. June 8, 1943 2,562,678 Okumura July 31, 1951 2,620,711 Lindsay Dec. 9, 1952 

